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THE EFFECTS OF CORNER RAD11 ON THE LOCAL
BUCKLING OF COLD-F'ORMED SECTIONS
ARASH NASSIRIRAD
A Thesis
in
SCWOOL FOR BUILDIlVG
Presented in partial fulfillrnent of the requirements
for the degree of Master of Applied Sciences (Building) at
Concordia Unimrsity.
Montreal, Quebec, Canada
September 1998
National Library 1*1 of Canada Bibliothèque nationale du Canada
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The author retains ownership of the L'auteur conserve la propriété du copyright in this thesis. Neither the droit d'auteur qui protège cette thèse. thesis nor substantial extracts fiom it Ni la thèse ni des extraits substantiels may be printed or otherwise de celle-ci ne doivent être imprimés reproduced without the author' s ou autrement reproduits sans son permission. autorisation.
ABSTRACT
THE EFFECTS OF CORNER RADII ON THE LOCAL BUCKltING OF
COLD-FORMED SECTIONS
ARASH NASSIRIRAD
In steel construction the methods to produce structural members include hot
rolling, forming and welding hollow section (HSS) and welding plates to
form 1's (WWF). Another method, which is less widely known but is
growing in acceptance, is cold-forming fiom steel sheet or strip using roll-
forming machines, press and bending brakes, or folding operations. These
cold-forrn steel sections have their own design codes.
The use of cold-fonned structures in building constructions goes back to
about the 1850s in both the United States and Great Britain but the forma1
design methods for these sections were developed only since 1940.
Cold-formed sections add aspects to the design procedure which are
neglected in codes for hot-rolled shapes, namely local and torsional
buckling. The elements of a box or channel section formed from thin sheet
may buckle locally, leading to collapse. To calculate the buckling stress the
iii
manufacturing process, makes the measurement of the width uncertain.
Codes simply adopt the flat width. The objective of this study is to develop a
more accurate method to predict the buckling stresses for two major kinds of
cold-formed section, namely an open section (channel) and a closed
section (box).
A theory has been developed to mode1 the elastic local buckling mode for
box and channel sections. This is extended to predict the behavior of the
section after buckling and up to the collapse. Cornparisons are made with the
results of the numeric analysis carried out using the finite element program
ABAQUS, and with the code requirements.
To Dr. Shahin Izadian
who supports this study by her life and spirit.
ACKNOWLEDGrnNTS
The author wishes to express his gratitude to ProfessorCedric Marsh, for the
initial encouragement in the project, and for his continuous guidance and
suggestions, which have enriched the content of this work.
The author is also grateful to his colleagues, for their valuable criticism,
helpful advice and solid support.
Financial support fiom NSERC is also acknowledged.
TABLE OF CONTENTS
LIST OF FIGURES
LIST OF TABLES
LIST OF SYMBOLS
DEFINITIONS
CHAPTER 1
INTRODUCTION
1.1 General
1.2 Behavior of cold formed members
1 -2.1 Rectangular box columns
1.2.2 Channel columns
CHAPTER 2
THEORETICAL MODEL
2.2 Overall buckling
PAGE
xi
xiv
xv
xix
vii
2-2 Box section
2-2-1 Code procedures
2.2.2 Proposed analytical model
2.2.3 Theoretical post-buckling
2.3 Channel section
2.3.1 Code procedures
2.3.2 Proposed analytical model
2.3.4 Theoretical post-buckling
CHAPTER 3
FINITE ELEMENT STUDIES
3.1 Introduction
3.2 Eigenvalue method
3.3 Ultimate load
3.4 ABAQUS program
3.4.1 Introduction
3.4.2 Input of the program
3 -4.3 Output of the program
viii
CHAPTER 4
COMPARJNG THE RESULTS
4.1 Typical example
4.1.1 Theoretical calculation
4.1.2 Code predictions
4.1.3 Finite element results
4.1.3.1 Eigenvalue result
4.1.3.2 Postbuckling strength
4.2 Results for box sections
4.3 Results for channel sections
4.4 Conclusions
4.4.1 Box section
4.4.2 Channel section
4.4.3 Final comments
4.4.4 Future research
APPENDIX 1
ANALYSIS
1.1 Introduction
1.2 Box section
1.3 Channel section
1.3.1 Flange mode
1.3.2 Web mode
APPErnIX II
WARPING CONSTANT
11.1 Box section
11.2 Channel section
APPENDIX III
List 1
List 2
FIGURES
TABLES
REFERENCES
1-1
1-9
1-9
1-1 3
II
II- 1
II- 1
11-4
III
III- I
111-4
F1
T l
R1
LIST OF FIGURES
Figure D-1 Local buckling for a box section
Figure D-2 Local buckling for a channel section
Figure D-3 Flat, overall and effective widths
Figure D-4 Collapse mode for a box section
Figure D-5 Warping for 1 beam
Figure 1 - 1 Cold-formed sections
Figure 1-2 Cold-forrned steel structure
Figure 1-3 Cold-formed and hot-rolled steel structure
Figure 1-4 Typical cold-formed panels
Figure 1-5 Force-shortening relationship for column and plate
Figure 1-6 Box and panel section dimensions
Figure 1-7 Stress distribution on a simply supported plate
Figure 2-1 Buckling and postbuckling strength
Figure 2-2 Cold-formed and hot-rolled corners
Figure 2-3 Simply Supported plate
Figure 2-4 Postbuckling curve
Figure 2-5 Buckling modes of a channel
Figure 3- 1 Sarnple plate for ABAQUS
FD- 1
FD-2
FD-3
FD-4
FD-5
f1-1
f1-2
f1-3
F 1-4
f1-5
F1-6
Figure 4-1 Typical box section
Figure 4-2 ABAQUS elastic buckling
Figure 4-3 Stress distribution across the wall of a box section
Figure 4-4 Mean stress and axial shorting for a box section
Figure 4-5 to 4-34 Critical and ultimate stress for box sections
Figure 4-35 to 4-37 m factor for box sections
Figure 4-38 to 4-40 Normalized m for box sections
Figure 4-4 1 Normalized mean postbuckling strength for box sections
Figure 4-42 to 4-56 Critical strsss for channel sections
Figure 4-57 to 4-59 m factor for channei sections
Figure 4-60 to 4-62 Nomalized m for charme1 sections
Figure 4-63 Normalized mean strength for channel sections
Figure 1-1 Deflection of a box section
Figure 1-2 Deflection of a channel section (flange mode)
Figure 1-3 Deflection of a channel section (web mode)
Figure 11-1 Corner of a box section
Figure 11-2 Warping constant construction for the corner of a box section
Figure 11-3 Warping constant for box sections
F4- 1
F4-2
F4-3
F4-4
F4-5 to F4-34
F4-35 to f4-37
F4-38 to F4-40
F4-4 1
F4-42 to F4-56
F4-57 to f4-59
F4-60 to F4-62
F4-63
FA- 1
FA-%
FA-3
FA-4
FA-5
FA-6
xii
Figure 11-4 Warping factor a for box sections FA-7
Figure 11-5 Corner of a channel section FA-8
Figure 11-6 Warping constant construction for the corner of a charme1 section FA-9
Figure 11-7 Warping constant for channel sections FA-10
Figure 11-8 Warping factor a for channel sections FA-1 1
xiii
LIST OF TABLES
Table 4- 1 Summary of results for box sections
Table 4-2 Sumrnary of results for channel sections
xiv
LIST OF SYMBOLS
Unreduced cross-sectional area of section
Effective cross-sectional area of section
Plate rigidity
Elastic modulus
Elastic buckling force
Ultimate force
Ultimate load from ABAQUS
Warping constant
Factor
Elastic stiffness matrix
Initial stiffhess matrix
Length
Bending moment
Axial flux
Loading pattern matrix
Bend radius to median line
Strain energy due to bending
Strain energy due to warping
Strain energy due to bending of web
External work
Work done by applied stresses
Axis
Axis
Axis
Shorter width of the box and width of the web of a channel
Deflection coefficients
Longer width of the box and width of the flange of a channel
Effective width of the box and flange of a channel
Halfwave length of a buckied element
Distance to shear centre
Factor
Normalized m factor
True length of section
Thickness
Displacement in X direction
xvi
Increment in displacement for load-displacement control
Displacement in Y direction
Flat width
Flat width limit
Distance along X axis
Distance along Y axis
Distance along Z axis
Warping factor
Angle of rotation
Factor
Deflection matrix for eigenvalue
Angle of twist at the corner
Buckling mode matrix for eigenvalue
Slenderness
Normalized slenderness
Load multipliers for eigenvalue
Poisson ratio (0.3 for steel)
Stress
xvii
ABAQUS o a v
ABAQ US O c r
Normalized stress
Actual buckling stress
Elastic buckling stress
Actual buckling stress for web of channel section
Yield strength
Average ultimate stress fkom ABAQUS
Elastic critical stress fiom ABAQUS
xviii
DEFINITIONS
LOCAL BUCKLING shown in Fig D-1 for box and Fig D-2 for a
channel is a wavelike deflection form, with a wavelength
independent of the overall length.
CORNER RADIUS: is the radius of the median line at the corners
of a formed section. It is usually a multiple of the thickness.
CRITICAL FORCE (STRESS): is the force (stress) which causes
initial elastic buckling of a member or element.
EFFECTIVE DESIGN WIDTH (b,,): is the width assumed to carry
the yield strength, used to calculate the collapse load.
FLAT WIDTH (w): is the width of the straight portion of the
element, Fig D-3.
LZMITING WIDTH/THI:CKNESS RATIO (w/t): is the
widWthickness ratio below which local buckling need not be
considered.
OVERALL WIDTH (b): is the overall width of the element
between points of intersections of the median lines, Fig D-3.
xix
ULTIMATE FORCE: is the load which causes the member to
collapse, as shown in Fig D-4
WlDTH/THICKNESS RATIO: is either the "flat width ratio"
which is the ratio of the flat width (w) to the thickness (t) or
bboverall width ratio" which is the ratio of the overall width (b) to
the thickness. (Fig D-3)
0 WARPING: when twisting in open sections causes translation in the
planes of elements of the section, the cross sections tend to warp
from the original flat plane, as shown inFig D-5. If this warping is
resisted it contributes to the torsional stiffhess.
m YIELD: is the stress at the limit of the elastic range, or at a 0.2%
permanent offset strain.
CHAPTER 1
INTRODUCTION
1.1 GENIEIRAL,
Cold-formed steel sections represent an alternative to hot rolled sections in
applications where the light weight sections can be used.
Although the use of cold-formed sections in construction has been known
since the middle of the last century the use of cold formed members in
buildings was fonnalized with the publication of "Specification for the
Design of Cold-Forrned Steel Structural Members" by the American Iron
and Steel Institute (AISI 1946) which was the first to provide a fomal design
procedure base on the seminal work of Winter (1937 ). The most recent AIS1
code is "Specification for the design of cold-fomed steel structural
mernbers" (1996). The first Canadian standard, "The Design of Light Gauge
Steel Structural Members" appeared in 1963, while the latest CSA-S 136-
M94 "Cold formed steel structural members" was issued in 1994.
The Arnerica Society of Civil Engineers (ASCE) prepared a standard
ANSYASCE 8-90 "Specification for the Design of Cold-Formed Stainless
Steel Structura1 Members" in 1990.
By using cold foming it is possible to produce more efficient structural
shapes, which have been used extensively in airplanes and car bodies, but in
the construction industry the use was limited to roofing sheet and panels.
Over the past 40 years, several studies for the design of thin walled sections
have led to an increasing use of cold-formed steel in building structures.
Open sections used as wall studs, floor and roof beams are found in
institutional, commercial , residential and light factory buildings. Storage
racks and latticed joists incorporate special cold fonned shapes.
The major difference between cold-formed sections and hot-rolled sections
is the relative thickness, or (b/t) ratio, which leads to the following
advantages:
Cold-formed members c m be manufactured more easily.
Unusual sectional configurations can be produced economically and
consequently, more favorable strength-to-weight ratios can be
obtained.
Nesting sections can be produced, allowing for compact packaging
for shipping.
Great accuracy of the profile
r A wider variety of shapes
A wider variety of steel tempers
Coated and painted sheet
a Sections c m be perforated
Cold-formed steel structural products can be classified into two major types:
Individual structural fiaming members.
m Panels and decks.
Fig 1-1 shows some of the cold-formed sections generally used in structural
fiarning. The more usual shapes are channels, 2-sections, angles, hat
sections.
In general the thickness of cold-formed rnembers ranges fkom 1 to 10 mm.
In view of the fact that the major function of this type of individual h i n g
member is to cany load, structural strength and stiffhess are the main
considerations in design. Such sections can be used as primary fiaming
members in buildings. Fig 1-2 shows a two-story building framed using
cold-formed steel sections. In ta11 multistory buildings the main fkaming is
typically of heavy hot-rolled or welded sections, to support the primary
loads, while the secondary elements such as studs and joists (Fig 1-3) may
be of cold-forrned steel to support secondary loads.
Typical cold-formed panels are shown in Fig 1-4. These products are
generally used for such items as roofs, floor decks, wall panels, siding
material, and concrete forms.
1.2 BEHAVIOUR OF COLD FBRRIED MEMBERS
The current approach to the design of structures is based on a limiting stress
dictated by the proportions of the section. This limiting stress is related to the
mode of failure which may be governed by any of a number of factors.
Tension mernbers under static loads can fail by general yielding of the cross
section or rupture at the net section. Members in axial compression may
reach their maximum strength by yielding, by local buckling of thin
elements, or by overall buckling in flexure or torsion, or by a combination of
modes. Members in bending may be controlled by yielding, mpture at a net
section, local buckling or lateral buckling.
The study concentrates on two cornmon cold-formed sections which belong
to separate categories:
1. The behaviour of a box section is used to represent flat elements in formed
panels, and channel webs, where the elements are supported along both
long edges.
2. The channel section, in which the flange represents an element supported
along one long edge only.
In al1 cases of buckling, the critical elastic stress, O,, is given by:
where
E : elastic modulus A: slenderness ratio
= KL/r for flexural buckling in columns = mb/t for local buckling of plate elements
b: width K: a factor related to flexural buckling L : length m: a factor related to local buckling r: radius of gyration t: thickness
For an axially loaded column failing in flexure or torsion, the critical load is
the ultimate load and the theoretical forcelshortening relationship is as
shown in Fig 1-5 curve 1. In the case of flat elements supported along both
long edges which posses postbuckling strength, the theoretical force1
shortening relationship is shown in Fig 1-5 curve 2.
1.2.1 RECTANGULAR BOX COLUMNS
The ultimate axial compressive strength of a rectangular box colurnn is
govemed by either overall buckling or local buckling. Overall buckling leads
to collapse, but after initial local buckling of the flat elenients there is a
reserve of strength.
The initial stress to cause elastic local buckling is given by:
For a uniform axial stress, on a square box section, m=1.65 (CSA-S 136-94)
The dimensions used are shown in Fig 1-6.
Up to initial local buckling, the forcekhortening relationship is assurned to
be linear and the stress is assumed to be uniformly distributed over the cross
section. After buckling, the behaviour changes:
The relation between force and shortening is nonlinear
The distribution of stress over the section is not uniforrn but takes
the form shown in Fig 1-7.
The local deflection of a buckled element becomes large
The applied force can be increased until the yield strength is
reached at the corners of the section.
1.2-2 CHANNEL COLUMNS
Channels are open sections with only one axis of symmetry. In this case
failure may be by local buckling of the flanges, overall flexure or torsion, or
by a combination of these. Buckling in any of these modes precipitates
collapse.
The flange of an open section, such as in a charnel, is considered to be an
unstiffened element, supported along only one longitudinal edge.
Local buckling of the flange is given by equation (1.2) with a value of m
between 3 and 5 depending on the ratio of the flange width to the web depth.
If the flange buckles first, in a pin ended member, the section cannot cany
more load and this critical buckling load can be assumed to be the ultimate
load. However, if the web buckles first, the element c m cany more load, as
in a box section.
CHAPTER 2
THEORETICAL MODELS
In this chapter the current design methods, taken fiom CSA S 136-94 "Cold
formed steel structural members", which is typical of such Codes in general,
are introduced, followed by a description of the analytical mode1 used in this
study for plates with one or both longitudinal edges supported, representing
the flanges of channels and the walls of boxes.
2.1 OVERALL BUCKLING
For overall flexwal buckling, CSAS 136-94 uses a relationship between the
elastic critical stress, o;,, and the actual buckling stress, cc, given by:
When normalized this becomes:
where
The curve is shown in Fig 2-1. In this figure the CSA Code result for plate
and column are compared with this thesis theory and von Kannan's results.
2.2 BOX SECTION
2.2.1 CODE PROCEDURES
The manufacture of cold-formed section requires a radius at each corner.
(The form of radius differs for that in hot-rolled sections as shown in Fig 2-2)
In today's design codes the influence of this radius is to reduce the width to
the "flat width", which is used in design.
In a11 the current codes for strength design in cold-formed steel the following
procedure is adopted for walls with both long edges supported:
a For al1 proportions of the cross section, local buckling is treated by
considering the flat elements to be joined together at the corners
with simply supported edges.
Only the flat width (w) is considered to buckle locally.
Below a specified limit for the flat width (w') there is no buckling.
For greater widths, after initial local buckling, zones at the edges of
the flat width are assumed to carry the yield strength. (The sum of
these two zones is called the "effective width", b, )
Radiused corners are assumed to carry the yield strength, but are
otherwise disregarded
The critical buckling stress is given by (CSA S 136-94) :
Using Poisson's ratio, v=0.3, this gives:
A = 1.65(%)
The critical axial force for the flat width is then:
where
A = w t
To calculate the ultimate force, the Codes introduce an effective width
which can carry the yield strength, based on a formula proposed by Winter
(1 967), given below in its normalized fom (ASCE-8-90):
for 3 < 0.673, bfl = w
for n > 0.673, bg = p w
where:
The ultimate force on the "flat width" for a singular plate is then given by:
The four walls of a square box will thus resist a total ultimate force:
That the "flat width" should be used was the result of a cornmittee decision
based on an intuitive feel for behavior but with no support fiom theoretical
or experimental evidence.
This study undertalces to show the true influence of the radius, and, also, of
the influence of adjoining elements.
2.2.2 PROPOSED ANALYTICAL MODEL
To obtain theoretically the critical stress, a rectangular box with the
foilowing dimensions is considered:
a: shorter width of box b: longer width of box c: halfwave length of buckled element R: radius at the corner t: thickness
The box is assumed to be subjected to a uniform axial stress. The energy
method, (Timoshenko and Gere (1961)), in which the total strain energy of
distortion of the plates is equated to the work done by the axial stress in the
longitudinal direction as buckling occurs, is used to obtain the local initial
elastic critical stress.
The strain energy has two components:
m That due to deflection of the plates
r That due to twisting at the corners
The strain energy due to bending of the plate of width b, supported on al1
edges, can be written in terms of the deflections as follow: (Fig 2-3)
(Timoshenko, The terms related to twisting is equal zero in box sections)
where w is the deflection at the point (x,y) and D is the plate flexural rigidity
given by:
The strain energy due to twisting at the corners is calculated based on the
resistance to warping of the radiused portion.
The general form of strain energy due to warping is (Timoshenko) :
where H is the warping constant and:
The work done by the compressive extemal force as the elements shorten
during buckling is given by:
in which N is the load per unit width of the section.
The change in strain energy in the member is equal to the work done, thus:
U B + U H - T = O (2.18)
U, ,&,, and T are for the total section.
This is a minimum energy state. Differentiating equation (2.16) with respect
to the coefficients a, and a, and equating the results to zero, gives two
equations. The determinant of these two equations is theii equated to zero
and solved for N.
The deflected shape of each wall of the box is assumed to be given by an
expression of the form:
The cosine term represents the influence of the corner restraint. The
complete procedure to obtain the theoretical critical stress is presented in
Appendix 1.
2.2.3 THIEORETICAL POST-BUCKLING
The above analysis deals with elastic buckling and gives the critical stress.
After exceeding this stress the deflection increases rapidly, but the plate can
support the increasing load by a redistribution of the stress. The limiting
capacity is reached when the stress at the supported edges reaches the yield
strength. An approximate expression that determines the ultimate load is
represented below.
The theory assumes a perfect plate and linear material behaviour, but real
plates are not completely flat before loading and materials are nonlinear as
the yield strength is approached. The result is that the deflection increases
from the beginning of the load application, and buckling is not a sharp
action, furthermore the stress distribution is not unifonn fi-orn the beginning
of loading, with higher stress at the edges. The tme initial buckling stress,
cc, differs fkom the ideal elastic value, a,, and is given by a curve based on
experiments, of the forrn shown in Fig 2- 1, taken fkom CSA-S 136-M94 for
columns.
After buckling the stress distribution is shown in Fig 1-7 and the total load is
given by:
which is the area under the actual stress distribution curve. It can be seen that
in the limiting condition the plate may be approximated by two strips
carrying the yield strength as describe in 2.2.1.
In the general case, the width of plate, when the critical stress is equal to the
yield strength, is obtained fiom:
fiom which:
The total axial force on the flat plate is then oYb , r . Von Karman (1940)
proposed that this value of the axial force remained constant for al1 greater
values of b, thus when b>b, the mean axial stress at the ultimate load is:
From tests, this expression has been shown to be unconservative. It is
proposed to replace a, by the true buckling stress oc fiom the buckling
curve shown in Fig 2-4.
The normalized average stress can then be expressed by:
and the ultimate force is given by:
The resulting relationship is compared with the code formula [Winter
(1967)l in Fig 2-4
In this study it is proposed that in the general case the ultimate load is given
in which the buckling stress, O,, will be that for the element of the box,
taking into account the corner radius and the adjoining walls, and s is the
total length of the walls:
2.3 CHANNEL SECTION
2.3.1 CODE PROCEDURES
A channel section is considered to be an assembly of individual plates
simply supported at al1 edges except at the fiee edges of the flanges. In this
way the design is simplified to the design of one plate simply supported on
both long edges and two plates simply supported along one long edge and
fkee the other.
The current method used in Canadian codes is based on the effective areas of
these individual plates. The following procedure is adopted:
Only the flat widths (w) are considered to buckle locally.
The corners are treated as simple supports.
Below a specified limit for the flat width there is no buckling.
Q For greater widths, after initial local buckling, zones at the edges of
the flat width are assumed to carry the yield strength.
Radiused corners are assumed to carry the yield strength but are
othenvise disregarded.
0 The web of a channel is treated in the sarne manner as the elements
of a box section.
For flanges, called "unstiffened elements", the critical buckling
stress, neglecting any restraint by the web, is given by (ASCE-8-90)
Using Poisson's ratio, v=0.3, this gives:
2.3.2 PROPOSED ANALYTICAL MODEL
The following dimensions are used for obtaining theoretically the critical
stress of a channel:
a: flange width b: web width c: halfwave length of buckled element R: radius at the corner t: thickness
As with the box channel the energy method is used to obtain the critical
stress. The strain energy is supplied by:
a Deflection of the web, u,
Bending and twisting of the flange, U,
a Twisting at the corners, UT
The change in strain energy in the member is equal to the work done, thus
(Timoshenko) :
The complete procedure for finding the theoretical critical stress is presented
in Appendix 1.
Should the ratio of the web depth to the flange width exeed three, for
uniform stress, the web is less stable than the flange,and it is restrained by
the flanges. This is shown as the "Web Mode" inFig 2-5. For smaller ratios,
the flange is less stable and is restrained by the web shown as the ccFlange
Mode" in Fig 2-5.
2.3.4 THEORETICAL POST-BUCKLING
Up to this point the analysis has been concerned with the theoretical local
elastic buckling stress. In a concentrically loaded column, flange buckling
leads to collapse at the critical local buckling stress as there is no
rnechanism to develop postbuckling strength.
If the web buckles first it possesses postbuckling strength and the average
limiting strength for the web area based on the box section calculation,
becornes:
where o, i s the actual buckling stress for the web obtained fkom equation
2.2, using  for the web with m=1.65.
CHAPTER 3
FINITE ELElMENT STUDIES
3.1 INTRODUCTION
The more complex a section is, the more difficult is evaluation with
theoretical analysis. This is the reason that, today, many plate stability
problems in practical engineering are evaluated by numerical methods such
as the finite element method, which give approximate solutions for the ruiing
equations. In the finite element method the exact differential equation at a
point is replaced by an algebraic expression consisting of the value of the
function at that point and at adjacent points. In other words, the analytical
solution describes the behaviour of the systern as a continuous system, while
the finite element solution gives an discrete solution of the function. In
general if a continuous system is replaced by a discrete system the analytical
function is replaced by numerical values which represent the function at each
point.
In this study finite element methods provide a means to obtain an
independent check on the results of an analytical approach and on the
validity of code procedures. Box and charnel sections were analyzed using
the FEM program ABAQUS to obtain:
The critical elastic buckling stress using the Eigenvalue method
0 The ultimate, postbuckling capacity, using controlled displacement
3.2 EIGENVALUE METHOD
The eigenvalue represents the ideal elastic critical stress for initial buckling,
and is used here to compare the values obtained for different boundary
conditions. The formation of the eigenvalue problem is based on stability
analysis. The procedure may be stated as follows. Given a system with an
elastic stifkess matrix (K:: ), a loading pattern defined by the vector (eM ),
and an initial stress and load stifhess matrix (K"), find load multipliers
(A,), and buckling mode shapes @y), which satisfy:
in which N and M refer to degrees of the fieedom of whole system and i
refers to the ith mode. The critical buckling loads are then given by CZ,QM).
Usually only the smallest load multiplier and its associated mode shape are
of interest.
As an illustration
supported plate is
of the procedure of the eigenvalue method a simply
considered. Assume a square thin elastic plate, simply
supported on al1 four edges is loaded by an axial compression force in one
direction. (Fig 3-1)
The plate is divided into 20 elements (eight-node elements with 4 node on
the corner and 4 node on mid points). Due to symmetry, only a quarter of the
plate need to be considered. Briefly, the elastic sti&ess matrix[k,,], is
formed by adding al1 the element stiffness matrices which is given by:
in which [6] is the matrix of the deflection on 4 nodes of the element:
[4] , [a] are given by:
[Dl is the material constant matrix:
and N is the external work matrix on the element, given by:
Consequently to detennine the critical load it is necessary to obtain the non-
zero solution of:
{[k, 1 - 1% ImI = 0 (3.8)
in which [A] consists of the section nodal defiections and [Il is the index
matrix.
This is done by setting the determinant of the matrix equal to zero and
solving for the smallest root of the resulting equation.
3.3 ULTIMATE LOAD
To determine the collapse load for shells, a load -displacernent analysis is
performed. This checks that the eigenvalue buckling prediction is accurate
and at the sarne time investigates the behavior after buckiing, and up to the
collapse load.
The collapse load is defined as the maximum value in the load -
displacement curve. To find the maximum load, a stepwise increasing load
or displacement is applied. If the applied load is incremented it is called
"load control", and if the axial shortening is incremented it is ca-lled
"displacement control". Briefly, for "load control" an equilibrium system is
assumed to which a srnaIl increment of load is added. This unbalance causes
a displacement in the system which c m be represent as:
where u, , is the initial displacement and A U , is a small increment which can
be evaluated based on the incrernent in load.
This displacement becomes the initial displacement for the next step with a
new load incrernent. It is the sarne process for "displacement control" by
assuming steps in displacement.
3.4 ABAQUS PROGRAM
3.4.1 INTRODUCTION
The program which is used for numeric evaluation is ABAQUS. This
program is a general finite element program. It is an interactive preprocessor
used to create finite element models for shells. It has a variety of analysis
types. Those of the interested in this study are eigenvalue extraction and
static stress analysis, which are used for pre- and post-buckling. The program
accepts the input which includes:
Mode1 Data
History Data
The data to define a finite element model are:
the elements: number, properties
nodes: number
material properties
History Data represents the initial condition or sequence of events or loading
for the model. History data for eigenvalue method is basically an arbitrary
initial load based on this method, and has only one step. For load -
displacement analysis it represents the properties at each step which include
both load and displacement.
3.4.2 INPUT OF THE PROGRAM.
For executing the program, based on the method used, the following input is
required:
DEFINING OF MODEL:
Elements and Nodes: The number and type of element (classified
by the number of nodes in each element
Shell: The elernents in each shell and the nurnber of layer in each
shell with their thicknesses.
Material: The elastic modulus, yield strength and Poisson ratio for
each layer of the shell
Boundary and Symmetric Condition: The conditions on each
boundary and any syrnmetry
DEFINING OF HISTORICAL DATA
Eigenvalue method: An initial stress distribution on the specific
boundary is required. (Appendix III- List 1)
Load - Displacement analysis : In case of Load Control an initial
and a step increment stress distribution on the required elements.
For the case of Displacement Control an initial and a step increment
strain distribution on the required elements. (Appendix III- List 2)
3.4.3 OUTPUT OF THE PROGRAM:
For each case by executing the eigenvalue section of the program, ABAQUS
predicts the buckling modes and corresponding eigenvalue. Also a list of
stresses and deflections is provided in the output of the program.
The load-displacement analysis results for each case are typically provided
in n steps fiom zero load to a maximum which is part of the input. At each
step the stress and strain distribution over the section is provided in the
output.
CHAPTER 4 COIMPARING THE RESULTS
The numerical, finite element results are compared with the theoretical
predictions and the Codes rules. The fhite elernent study was made for box
and channel sections in the following ranges:
BOX SECTION RANGE
Ratio of widths, a h (a < b): 0.25,0.5, 1 Ratio of width / thickness, b/t 40, 50, 66, 100, 200 Ratio of corner radius / width, R h O to a/2
CIXANNICL SECTION
Ratio of web / flange width, ah 1, 2, 4 Ratio of flange width / thickness, b/t 40, 50, 66, 100, 200 Ratio of corner radius / flange width, Rh O to b/2
4.1 TYPICAL EXAMPLE
To show the procedure for each case the following typical box section is
chosen (Fig 4-1):
4.1.1 'l'TE0RETICA.L CALCULATION
D is given by:
Warping factor a=0.044, and the warping constant H is given by (see appendix II for details):
The elastic critical stress obtained fiom the theoretical analysis is:
The norrnalized slenderness is:
Thus, - according to the CSA standard, the tme buckling stress for h > Vd0.6 = 1.29, is:
The predicted mean stress at collapse, according to the method proposed in this thesis (Equation 2.24) is then:
The true length of the walls is:
Then the collapse load is:
4.1.2 CODE PREDICTIONS
The flat width is :
w = b - 2 R = 1 0 0 - 2 x 5 = 9 0 mm
giving a slendemess of :
f = 1 . 6 5 % = 1 . 6 5 ~ 9 0 ( = 1 4 9
The critical buckling stress is given by:
Leading to:
and:
The ultimate load fiom the Code is given by:
Thus the predicted average stress at collapse is:
4.1.3 FINITE ELEMïENT RESULTS
4.1.3.1 EIGENVALUE RES'ILTLT
The eigenvalue is detennined using load-control. Based on the input shown
in Appendix III-List. 1 the elastic critical stress for this case is (Fig 4.2):
4.1.3.2 POSTBUCKLING STRENGTH
The ultimate load is determined using displacement contro1,Appendix III-
List.2 shows the input format. At each step, the stress distribution across the
boundary element set is obtained, and the average stress is evaluated. For the
typical example being demonstrated, the stress distribution across the section
at the ultimate load is shown in Fig 4.3.
Fig 4.4 shows the relationship between the mean stress and axial shortening.
The highest stress in this curve represents the ultimate average stress,
which is:
The ultimate force is given by:
F~;""~*' = a ; l b lSAPUSst =162~391~1=63500N
4.2 RESULTS FOR BOX SECTIONS
The results are given in the figures listed in following table:
Fig 4.5 Fig 4.6 Fig 4.7 Fig 4.8 Fig 4.9 Fig 4.10 Fig 4.1 1 Fig 4.12 Fig 4.13 Fig 4.14 Fig 4.15 Fig 4.16 Fig 4.17 Fig 4.18 Fig 4.19
Fig 4.20 Fig 4.21 Fig 4.22 Fig 4.23 Fig 4.24 Fig 4.25 Fig 4.26 Fig 4.27 Fig 4.28 Fig 4.29 Fig 4.30 Fig 4.3 1 Fig 4.32 Fig 4.33 Fig 4.34
Critical Critical Critical Critical Critical Critical Critical Critical Critical Critical Critical Critical Critical Critical Critical
Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate Ultimate ültirnate Ultimate
In ench figure the Code, theory and ABAQUS result for critical and ultirnate stresses are shown. Table 4-1 shows the summary of the results for al1 the cases. In this table how the Code and the theory differ fiom ABAQUS is shown as a percentage error. The m factors used in equation 1.1 are represented in Fig 4-35 to 4-37, and values normalized with respect to 1.65, for box sections, are shown in Fig 4-3 8 to 4-40, as they Vary with Rh.
Finally following figure shows the normalized mean stress at the ultirnate load for theory, ABAQUS and Code predictions.
Normalized column buckling stress
1
0.8 0 ABAQUS O - Code
- Theory
The extreme cases based on the percentage error between Code and ABAQUS result are s h o w in following table:
a h
1 0.25
4.3 RESULTS FOR CHANNEL SECTIONS
The results are given in the figures listed in following table:
a/b
1
Fig 4.42 Fig 4.43 Fig 4.44 Fig 4.45 Fig 4.46
Fig 4.47 Fig 4.48 Fig 4.49 Fig 4.50 Fig 4.5 1
Fig 4.52 Fig 4.53 Fig 4.54 Fig 4.55 Fig 4.56
b/t
40 200
Critical Critical Critical Critical Critical
Critical Critical Critical Critical Critical
Critical Critical Critical Critical Critical
b/t
200
R/b
0.3 0.1
0.25 1 200
Rh
0.3 0.125
Critical wmm2) stress
Code
Error -79% 65%
Code 2832 28
Ultimate (N/mmz) stress
Theory
Emor 9% 11%
Code
Error -20%
Code 174 106
Theory 1435 72
Theory
Error 7%
40%
ABAQUS 1578 81
10%
Theory 134 160
ABAQUS 145 177
In each figure the Code, theory and ABAQUS predictions for critical stresses are shown. Table 4-2 shows the summary of the results for al1 the cases. In this table how the Code and the theory differ fiom ABAQUS is shown as percentage errors . The m factors are represented in Fig 4-57 to 4-59 and normalized values with respect to 5 for the flanges, are shown in Fig 4-60 to 4-62 as they Vary with Wb. Finally Fig 4.41 shows the normalized mean stress ai the ultimate load for theory, ABAQUS and Code results.
The extreme cases based on the percentage error between Code and ABAQUS result are shown in following table:
1 a h ( b/t ( Rh 1 Critical (N/mm2) 1 Code Theory L 1 200 0.1 Error 78%
stress ABAQUS 74
Code 16
Theory 69
4.4 CONCLUSIONS
4.4.1 BOX SECTIONS
The influence that the radii at the corners has on the elastic and ultimate
buckling stress of the box sections is important and should not be neglected,
as in the current codes.
For boxes with a low width to thickness ratio, 66 or less, failure occurred
close to the yield strength. In these situations the buckling stress is more
influenced by the ratio of the widths, (ah) than Wb. For a high width to
thickness ratio, more than 66 when the failure stress is lower than yield
strength, both the ratio of the widths and R h are very influential on the
failure. By neglecting the bla ratio and R h the Code c m be 65%
consenrative to 79% unsafe.
4.4.2 CHANNEL SECTIONS
The influence that the ratio of the web to flange, bla, has on the buckling
capacity of the section is important and must be considered. For the channels
with a web to flange ratio less than 3 failure occurred by flange buckling
mode, and the critical stress represents the ultimate stress. For a web to
fiange ratio more than 3 web buckling occurred first. In this case there is a
possibility for the channel to carry an ultimate load in exceed of critical
elastic value. By neglecting the b/a ratio the Code can be varied fiom over
34% to 54% conservative while by neglecting Wb, the Code canbe 78%
consemative.
4.4.3 FINAL COMMENTS
An inappropriate interpretation of the ratio of the width for the cold-formed
sections and the neglect of the influence of the corner radii on the buckling
capacity as in the current codes, c m lead to unsafe design or overdesign.
4.4.4 FUTURE RESEARCH
To follow the present work, which is just done for two major forms of cold-
formed section (box, charnel) it is recommended that other be investigated.
APPENDIX I
ANALYSE
1.1 INTRODUCTION
In this chapter the steps of the procedure are described. The software
which is used for parametric calculation is Mathcad which has the ability
to solve algebraic equations. To obtain the result for each specific case
the numerical values of the parameters are substituted in the final
algebraic expressions.
1.2 BOX SECTION
After buckling the deflection of the elements is assumed to be rnodeled
by trigonometric expressions as follows: (shown in Fig 1.1)
where a,.a,,a,,a, define the buckled shape and a < b.
As it was explained in Chapter 2 the strain energy due to deflection in a plate supported on al1 edges, is given by :
Considering the affect of the corner radii on the width of the plates for side b the strain energy due to bending is given by:
in which p is given by:
P(+
and for side a it is given by:
. +4&a.a 3.a4.c4.EOi[fk$-] +48.. 4 2 . c ~ . m s [ 1 . w ( O a ] . r i n [ Z n q ] - a
The external work due to uniform axial force given by:
The external work for side b is given by :
The warping constant is given by:
Where is the net displacement normal to a cross section due to
warping and the length s is measured along the element wall.
(For evaluation of H see Appendix I I )
The strain energy due to warping for the corner between sides a and b is given by:
in which
This leads to:
The energy balance for the whole section is given by:
U a i - U b f U ~ - ( r a + T b ) a (1-1 4)
This equation has five unknowns, NSa 1.a2,83.a4. At each corner the
tangents to the deflected plates must be perpendicular to each other.
This provides the third equationwhich gives a, in terrns of a l :
" 1.; (1-1 5 )
Considering the bending moment for sides a and b, to provide equal
moments at the corner for both ' plates the following equation must be
valid:
Substituting the value of a, and ., in term of , leads to an equation
with three parameters. Differentiating with respect to ., and ., gives hivo
equations. To find the theoretical critical stress the determinant of these
equations is equated to zero.
Differentiating with respect to . , gives:
F 1 l(N1-a 1 +F 12(N).a Zt30
Differentiating with respect to ., gives:
Equating the determinant of equations 5-17 and 5-18 to zero leads to:
The critical theoretical buckling force is evaluated from F , l(N)
to F 22(N) as:
1.3 CHANNEL SECTION
For a channel section the procedure is divided into two phases.
Depending on the ratio of web width to Range width, the critical buckling
stress for the web may be srnaller or larger than the critical stress for the
flange. The true buckling stress is that of the combined section, but the
buckling mode rnay be described as "flange mode" or "web mode".
1.3.1 FiANGE MODE
Assuming the flange buckles first, the deflection of the elements after
buckling is given by: (shown in Fig 1.2)
Web :
~ X Y w webs[a sin(";) + s 2. (1 - oos(+))].sin(nt)
Flange:
flangr=[o-X + a (1 - cos(z))]-rinjw:)
where e , a l , a 2 , a 2 define the buckled shape.
The strain energy due to bending for the web is given by:
where:
For the flange the strain energy is given by:
The external work for the web is given by:
and for flange it is given by:
The strain energy due to twisting at one corner is given by:
in which
This leads to:
The energy balance for the whole section is given by:
web + 2.U fiange + H- (T web + 2.T flange)'* (1-35)
This equation has five unknowns N,B,a ,,a,,a:. At each corner the tangent
to the plates must be perpendicular to each other. Thus:
X B a 1 s b
Equal bending moment at the corner for both plate gives:
Finally by substituting the value of a 3 and 0 in term of a ,,a, ,leads to an
equation with three parameters and the rest of the procedure is the same
as that for the box section.
1.3.2 WEB MODE
Assuming the web buckles first, the deflection of the elements after buckling
is given by: (shown in Fig 1.3)
Web :
where e , a l , a , , a l define the buckled shape.
The strain energy due to bending for the web is given by:
and for flange it is given by:
The external work for the web is given by :
and for flange it is given by:
The strain energy due to warping for a corner is given by:
Using the equations 1-41 and 1-44 and substituting the values of a, and
0 in term of al,a2 leads to an equation with three parameters, and the
rest of the procedure is the sarne as that for the box section.
APPENDIX II
WARPING CONSTANT
Each radiused corner of a box or channel section possessesa
warping constant which depends on the geometry of the section.
Based on the rnethod of ~imoshenko and Gere (1 961) the following
procedure is used to calculate the warping constant.
11.1 BOX SECTION
~ h e corner is opening up as shown in Fig 11.1. This is then treated
as a beam "loaded" by the normal distance from the intersection of
the median lines of the adjoining plates to the tangent to the corner
element, as shown in Fig 11.2. This normal distance is given by:
I=R- (sine + cos^ - 1) (11-1)
The total "load" is given by:
R and R , the reactions of the ends of the "beam", as shown in
Fig 11.2, are:
II- 1
The "shear force" in the beam is shown in Fig 11.2. This shear
force represents the term of (5,- a$ in the warping constant equation: . - - - - - - - - - - - . A -- -- - - - - - - -
The evaluation of this integral is based on two parts which are:
4 . lntegration on the straight parts
2. lntegration on the curve part
and H is given by:
The warping constant H can be expressed by (Fig 11.3):
in which:
b= longer length CL= a factor that varies with a/b and R/b shown in Fig 11.4
The value of a is given closely by:
11.2 CHANNEL SECTION
The corner is opened up as shown in Fig 11.5. The procedure is the sarne
as that for the box; however, in the channel section the centre of rotation
for the corner is no longer at the intersection of t h e median lines but at
a distance e from this point, on the rnedian line of the web, and is
- - - - - - - -- - - - - - - - - - - -establisried by niininiiting -the- YvaFpiig consfit as Toll6ws: -
The normal distance from the centre of rotation to t h e element tangent is
g iven by (Fig 11.6):
The total "load" is given by:
R, and R ~ , the reactions of the ends of the open corner beam, as shown
in Fig 11.6, are calculated using:
and
thus:
- - - - - - - A . - . . - - - - - -
force in the beam, as shown in Fig 11.6 represents the term of
the warping constant given by:
The evaluation of this integral is based on three parts which are (Fig 11-6):
i. lntegration on C part
2. lntegration on D part
3. lntegration on F part
1 (R 1 + e . ~ ) ~ dr P=.[(R 1 + e-b - e - ~ ) ~ - R 13]
O
where:
Lab-R
Differentiating the warping constant with respect to e, and equating it to _ _ _ _ _ _ _ _ _ - _ _ _ -_. _- _ - - - - - ---- - - - - - - - - - - - -
zero gives:
The warping constant H can be expressed by (Fig 11.7):
in which:
b= longer length a= a factor that varies with alb and Rlb shown in Fig 11.8
The value of a is given closely by:
APPENDIX III LIST-1 *HEADING SQUARE PLATE - ELASTIC BUDKLING ( BUCKLE )-S8R5 2 X 2 4-2-3-1 *restart, write *NODE 1010 1018,0.0,0.45,0.0 lOZ!4,O.O5,O.5,O.O 1032,0.5,0.5,0.0 2010,0.0,0.0,3.0 2018,0.0,0.45,3.0 2024,0.05,0.5,3.0 2032,0.5,0.5,3.0 1,0.450,. 050,O.O 2,0.450t .050,3.0 *NGEN, NSET=ZYEDGl 1010,1018,1 "NGEN, NSET=ZYEDG2 2010,2018,l *NGEN,NSET=ZXEDGl 1024,1032,l *NGEN, NSET=ZXEDGS 2024,2032,l *NGEN,NSET=ZRl,LINE=C 1018,1024,1,1 *NGENtNSET=ZR2,LINE=C 2018,2024,1,2 *NGEN,NSET=YZEDG 1010,2010,100 *NGEN, NSET=XZEDG 1030t2030, 100 *NFILL ZYEDGl,ZYEDG2,10, 100 *NFILL ZXEDGl,ZXEDG2,10,100 "NFILL ZRl,ZR2, 10,100 *ELEMENT, TYPE=S8R5, ELSET=ONE 1,1010,1012,1212, 1210, 1011, 1112, 1211, 1110 *ELGEN, ELSET=ONE 1, 11, 2, 1, 5,200, 11 "MATERIAL ,NAME=PLATE "ELASTIC 20.E4, . 3 *SHELL SECTION,MATERIAL=PLATE,ELSET=ONE .Olt 3 * BOUNDARY ZYEDG1,l ZYEDG1,Q ZYEDG1,G ZYEDG2,l ZYEDG2,4 ZYEDG2, 6 ZXEDG1,2 ZXEDG1, 5 , 6 ZXEDG2,S
ZXEDG2,5,6 ZR1,1,2 ZR1,4 ZR11 6 ZR2,1,2 ZR2,4 ZR1,6 YZEDG, YSYMM *STEP *BUCKLE 1,,,99 *MODAL FILE *CLOAD 1010t3,1.458 1011,3,5.833 1012,3,2.917 1013,3,5.833 1014,3,2.917 lOl5,3,S. 833 1016,3,2.917 lO17,3,5.833 1018,3,2.767 lOl9,3,5.236 1020,3, 2.618 1021,3,5.236 1022,3,2.618 1023,3,5.236 1024,3,1.726 1025,3,1.667 1026,3, O. 833 1027,3,1.667 1028,3, O. 833 lO29,3,l. 667 1030,3,0.833 1031,3,1.667 lO32,3, 0.417 2010,3, -1.458 2011,3, -5.833 2012,3, -2.917 2Ol3,3, -5.833 2Ol4,3, -2.917 2Ol5,3, -5.833 2Ol6,3, -2.917 2Ol7,3, -5.833 SOl8,3, -2.767 2019,3, -5.236 2020,3, -2.618 2021,3, -5.236 2022,3, -2.618 2O23,3, -5.236 2024,3,-1.726 2025,3, -1.667 2026,3, -0.833 2O27,3, -1.667 2O28,3, -0.833 2029,3, -1.667
2O3O,3, -0.833 2031,3, -1.667 SO32,3, -0.417 *NODE PRINT u *END S T E P
APPEHDIX III LIST-2 *HEADING SQUARE PLATE - RIKS STEP ANALYSIS ( STATIC )-S8R5 2 X 2 4-2-3-1 "restart, write *NODE 1010 1018,0.0,0.45,0.0 1024,0.05,0.5,0.0 1032,0.5,0.5,0.0 2010,0.0,0.0,3.0 2018,0.0,0.45,3.0 2024,0.05,0.5,3.0 2032,0.5,0.5001,3. O 1,0.450, .050,0.0 2,0.450, .050,3.0 *NGEN,NSET=ZYEDGl 1010,1018,1 "NGEN, NSET=ZYEDG2 2010,2018,1 *NGEN,NSET=ZXEDGl 1024,1032, 1 'NGEN, NSET=ZXEDG2 2024,2032,l "NGEN, NSET-ZR1, LINE=C 1018,1024,1,1 *NGEN, NSET=ZR2, LINE=C 2Ol8,2O24,l, 2 *NGEN,NSET=YZEDG 1010,2010,100 *NGEN, NSET=XZEDG 1030,2030,100 *NFILL ZYEDG1, ZYEDG2, 10,100 *NFILL ZXEDG1 , ZXEDG2,lOt 100 "NFILL ZRl,ZR2, 10,100 *ELEMENT, TYPE=S8R5, ELSET=ONE 1,1010,1012,1212, 1210, 1011, 1112, 1211, 1110 *ELGEN, ELSET=ONE 1, 11,2, 1, 5, 200, 11 *MATERIAL , NAME=PLATE "ELASTIC 20.E4, .3 *SHELL SECTION,MATERIAL=PLATE,ELSET=ONE .Olt 3 "BOUNDARY ZYEDG1, 1 ZYEDG1, 6 ZYEDGS, ZSYMM ZXEDG1, 2 ZXEDGl, 6 ZXEDG2, ZSYMM ZR1,1,2 ZR1,6 ZR2, ZSYMM YZEDG, YSYMM *STEP, NLGEOM, INC=400 "STATIC, RIKS t t t t1030t3t *2
*MODAL FILE "CLOAD 1010,3,. 0166666 1011,3, .O666666 1012,3, .O333333 1013,3,. 0666666 1014 13, -0333333 1015,3, ,0666666 1016,3,. 0333333 lOl7,3,. 0666666 1018,3, .O333333 1019,3,. 0666666 1020,3,. 0333333 1021,3, .O666666 1022,3,. 0333333 1023,3, .O666666 1024,3, .O333333 1025,3, .O666666 lO26,3, .O333333 1027,3, .O666666 1028,3, .O333333 1029,3, ,0666666 103013,. 0166666 *PRINT,RESIDUAL=NO *NODE filE, NSET=N2030 U *END STEP
Original flat shape
shape
Fig D. 1 Local buckling of a box section
FD- 1
Original flat shape
/ Deflected shape
Fig D-2 Local buckling for a channel section
FD-2
Overal width b, and flat width w
Effective width, b,,
Fig D-3 Flat, overall and effective widths
shape
Fig D-4 Collapse mode for a box section
FD-4
Twisting without restrain
Twisting with fixed end - - - - - - - - - - - - - - - - - - - - -
Fig D-5 Warping for 1 beam
Fig 1 - 1 Cold-fonned sections
FI-1
Fig 1-2 Cold-formed steel structure (Pen Meta1 Company)
FI-2
Fig 1-3 Cold-fomed and hot-rolled steel structure (Stran-Steel Corporation)
FI-3
Foor and roof panels
Long-span roof panls
Floor and roof panels
c - - Curtain wall panels Ribbed panels Comigatec panels
Fig 1-4 Typical cold-formed panels
FI-4
Fig 1-6 Box and panel section dimensions
FI-6
Variation of o, at plate edge
Fig 1.7 Stress distribution on a simply supported plate
Hot Rolled Section
Cold-Formed Section
Fig 2-2 Cold-formed and hot-rolled corners
Flange buckling mode
Web buckling mode
Fig 2-5 Buckhg modes of a channel
Fig 3 - 1 Sample plate for ABAQUS
F3-1
Fig 4-1 Typical box section
Fig 4-2 Typical ABAQUS elastic buckling
F4-2
E = 200000 ~lrnrn '
criticai-stress = 86 ~ l m m ~
ultimate-stress = 165 ~ l m d
Fig 4-4 Mean stress and axial shortening for each step for a box section
Fig 4- 19 Critical stress for a box section, &=OS blt=200
- TïIEORY --&--ABAGIUS --- CODE
[I) . * S m s u - h ~ $ I I * ,
c d :
i l : :
=? Tl-
Fig 4-46 Critical stress for a charme1 section, a/b=l b/t=200
Fig 4-63 Normalized mean strength for channel sections
T h e o r y 0 ABAQUS
N N X-Y-Z 45 degree view
N Down X axis Down Z axis
M M X-Y-Z 45 degree view
M Down Y axis D o m Z axis
Fig 1-1 Deflection of a box section
Flange:
N N N X-Y-Z 45 de- view Down X axis Down Z axis
Web :
M M M X-Y-Z 45 degree view Down Y axis Down Z axis
Fig 1-2 Deflection of a channel section (flange mode)
Flange:
N N X-Y-Z 45 degree view Down X axis
Web :
N Down Z axis
M M M X-Y-Z 45 degree view Down Y axis Down Z axis
Fig 1-3 Deflection of a channel section (web mode)
Fig II- 1 Corner of a box section
Loading distribution 1 R2
Shear force distribution
FigII-2 Warping constant construction for the corrner o f a box setion
Y +
Fig 11-5 Corner of a channel section
Loading distribution
Shear force distribution
Fig 11-6 Warping constant construction for the corner of a charnel section
Fig II-7 Warping constant for channel sections ( t-1 )
9000000 --
8000000 --
7000000 --
6000000 --
H 5000000 --
4000000 -- - aib=l design formula
3000000 -- - alb=0.75 - alb=O.5
2000000 -- X a/b=l by analysis U alb=0.75
1000000 -- a ahO.5
O O 0.05 0.3 0.15 0.2 0.25 0.3 0.35 0.4 0.45 0.5
Rlb
Table 4-1 Summary of results for box sections
Cc)
9 7
Table 4- 1 Sumrnary of results for box sections
Table 4-1 Surnrnary of results for box sections
Table 4- 1 Summary of results for box sections
Table 4- 1 Surnmary of results for box sections
Table 4- 1 Summary of results for box sections
Table 4-1 Sumrnary of results for box sections
Table 4- 1 Summary of results for box sections
Table 4-1 Summary of results for box sections
Table 4-1 Summary of results for box sections
Table 4-1 Summary of results for box sections
Table 4-2 Summary of results for channel sections
Table 4-2 Summary of results for channel sections
Table 4-2 Summary of results for channel sections
Table 4-2 Summary of results for channel sections
Table 4-2 Summary of results for channel sections
Table 4-2 Summary of results for channel sections
ABAQUS/STANDARD (Versi0n5.5)~ "Manual and Examples" Hibbit Karlsson & Sorensen, Inc. Email : hksGiWs.com
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